Varying motion planetary gear drive

ABSTRACT

This invention provides a simple mechanism for imparting a continuously Varying forward and reverse rotary motion to the ink fountain roller of a printing press. This roller is immersed in a wedge-shaped trough formed by an adjustable blade and the roller, and when filled with ink the flow of ink therefrom to a reciprocating ductor roller is regulated by the blade which is in close proximity with the fountain roller and the latter&#39;&#39;s angular velocity prevailing at the time the ductor roller is in contact therewith, and the ink collected by the ductor is then transferred to the distributing rollers of the printing press. This mechanism is also distinguished by having &#39;&#39;&#39;&#39;zero&#39;&#39;&#39;&#39; acceleration at the beginning and &#39;&#39;&#39;&#39;zero&#39;&#39;&#39;&#39; deceleration at the termination of its cyclic motion.

United States Patent 1 2,955,532 10/1960 l,8l8,555 'l,850,80l 3/1932 UNITED STATES PATENTS Seybold 1 y 1 Apr. 25, 1972 [s41 VARYING MOTION PLANETARY GEAR 3,565,006 2/1971 Stewart ...l0l/248 DRIVE 1 1 a a Primary Examiner-Clyde l. Coughenour [72] Inventor: Frederick W. Seyboldy l979 Dogwood I Drive, Scotch Plains, NJ. 07076 1 [57] ABSTRACT Filed: J y 7, 1970 This invention provides a simple mechanism for imparting a continuously Varying forward and reverse rotary motion to [21] Appl' 52962 V the ink fountain roller of a printing press. This roller is'immersed in a wedge-shaped trough formed by an adjustable [52] U.S. Cl. ..101/350, 74/394, 101/363, blade and the roller, and when filled with ink the flow of ink 118/262 therefrom to a reciprocating ductor roller is regulated by the [51] Int. Cl. ..B4li 31/04, Fl6h 35/02 bladewhich is in close proximity with the fountain roller and [58] Field of Search...; alm/350, 248, 363, 364, 366; the latters angular velocity prevailing at the time the ductor 74/394 roller is in contact therewith, and the ink collected by the ductor is then transferred to the distributing rollers of the printing [56] References Cited V press.

This mechanism is also distinguished by having "zero" acceleration at the beginning and "zero" deceleration at the termination of its cyclic motion.

6 Claims, 15 Drawing Figures PATENTEDAPR 25 1972 SHEET 1 [1F 5 PATENTED APR 2 5 I972 SHEET E OF 5 WMSW v m v SE8 mo 59? 383 3 0 20 4O 60 80 I00 I20 I I I 6 INPUT DEGREES Fig.l5

PATENTEDAPR 25 I972 SHEET 3 BF 5 INVIz'N'l'UR.

Kama m SW4 Fig.l4

Fig.4

VARYING MOTION PLANETARY GEAR DRIVE This invention pertains to a novel arrangement of an epicyclic gear drive in which one pair of the conventional two pairs of circular gears is replaced by a pair of elliptic gears one of which is secured to adjustable means. This arrangement of gearing may be employed in a variety of unrelated applications, one of which will be described in greater detail to demonstrate its versatility when used on the ink feed mechanism of a printing press.

Ink fountains comprising an intermittently rotating fountain roller actuated by a pawl and ratchet mechanism and in which the thickness of the layer of ink on the roller is regulated by an adjustable blade over which theroller turns are well known in the art.

From experience it has been learned that heat-set inks when used on high speed printing presses have a tendency to clog the exit of the ink between the blade and the fountain roller and thereby make it necessaryto stop the press and remove the accumulated matter.

However, a fountain roller receiving a periodic forward and then a short backward motion serves the purpose of removing such impurities from the wedge-shaped gap of the ink fountain.

Therefore, it is a primary object of this invention to provide means for imparting to the fountain roller a slight retrograde motion in addition to its cyclic forward motion.

A further object of this invention is to provide the means to impart a continuously varying rotary motion to the fountain roller ofa printing press.

Another object of this invention is to provide a means whereby the arc of contact of the ductor roller with the fountain roller can be varied considerably so that the ductor roller may take away more or less ink as required.

A still further object isto provide means for setting the fountain keys prior to starting a press run.

Another feature inherent in this mechanism is complete gear control so that a spinning ductor roller cannot turn the fountain roller preceeding its normal intermittent motion,

thereby eliminating holding pawls and brakes.

A further feature of this invention onthis reverted planetary gearing arrangement is the occurrance of zero acceleration at the beginning and fzero "deceleration at theztermination ofits cyclic motion.

Suitable applications for this invention would be indexing mechanisms, counting mechanisms, intermittent motions, single-stroke devices, one-revolution drives and oscillating motions with a minimum of shock. Conveyors on which a slowdown or momentary stop is desirable can readily be accomplished by the use ofthis invention.

FIG. I is a top view of the ink fountain roller drive mechanism, including the ink ductor motion;

FIG. 2 is an elevation view of the ink fountain roller planetary gear drive and sun gear rotation mechanism; FIG. 3 is a view showingthe ink ductor lever mechanism;

FIG. 4 shows the arrangement of the planetary gearing and driving arm;

FIG. 5 shows the relation between degrees input and corresponding motion of the planet elliptic gear;

FIG. 6 shows the angular velocity constant ofthe planet elliptic gearcorresponding to a position of the input driving arm;

FIG. 7 shows the angular acceleration coefficient of the planet elliptic gear corresponding to a position of the driving arm;

FIG. 8 shows the .angular'velocity of the output member corresponding to a position of the driving arm;

FIG. 9 shows the relation between degrees input and corresponding motion of the planet elliptic gear having a maximum angular velocity ratio of 2;

FIG. 10 shows the angular velocity constant of the planet elliptic gear corresponding to a position of the driving arm;

FIG. 11 shows the angular acceleration coefficient of the planet elliptic gear corresponding to a position of the driving FIG. 12 shows the angular velocity of the output member corresponding to a position of the driving arm;

FIG. 13 shows the arrangement of the planetary gearing and driving arm as employed in FIGS. 9, 10, 11 and 12;

F I6. 14 shows the arrangement of the planetary gearing and driving arm inwhich the two circular gears are of equal size, whereby oscillation of the output member is produced;

FIG. 15 shows the angular velocity of the output cor responding to a position of the driving arm and when the maximum angular velocity of the planet elliptic gear is 2.

GENERAL ARRANGEMENT The structural elements of the revertedplanetary gearing with said first elliptic gear andis compounded with a first circular gear of that set and journalled in said driving arm, and a second circular gear of that set meshing with said first circular gear and integral with a shaft of the output member, whereby uniform rotation of said driving arm will produce a varying angular motion of the output member.

The maximum velocity ratio A/B of the elliptic gears of FIG. 4 is 2.548, therefore, the minimum velocity ratio is the reciprocal of 2.548 or 0.393, see FIG. 6, and ifthe ratio C/D is 2/1 the output member will make one net reverse revolution per cycle and a slight forward motion.

ARM P l Hold 0 FIXED ELLIPTIC A OUTPUT D Assumethat in FIG. 4 the ratio A!!! is 2.00 and C/D is 2.00

Maximum speed of output is l (2 X 2) 3 Mean speed of output is I (I X 2) 1 Minimum speed of outputis l ('A x 2) =0 A change in the circular gear ratio affects the motion of the outputto a greater degree than a change in the elliptic gear ratio.

. The maximum velocity ratio MB of the elliptic gears of FIGS. l3and I4 is 2100, therefore,;the minimum velocity ratio is the reciprocal of 2.00 or 1/2, see FIG. 10.

, When the ratio C/D is 2/1 the output member will make one half revolution and comes to a stop and it attains a maximum velocity equal to three-fourths of the driving arm.

When the ratioC/D is 1/1 'theoutput shaft will oscillate, see FIG. 15. I Assume that in'FIG. I3 the'ratio A/B is 2.00 and C/D is 85, then the Minimum speed of output is l -(2 X Va) 0 Mean speed of output is l (I X It) k Maximum speed of output I --(V: X V!) "Vt Assume that in FIG. 14 the ratio A/B is 2.00 and CID is 1.00;

Using one of the circular gears as the stationary sun gear in place of the elliptic gear the resulting output shaft motions would be the same, as demonstrated below:

OUTPUT ARM P Fixed circular gear D" ELLIPTIC A" l I l HoldO 1 -(D/C B/A) Now assume that in FIG. 4 the circular gear D is held stationary and D/C V2, then Maximum speed of output is l (/2 X V2) A Mean speed ofoutput is I l -('/zX l/l)=+/z Minimum speed of output is l (/z X 2/1 Then assume that in FIG. 13 D/C 2/1 then Minimum speed of output is l (2}! X /z) 0 Mean speed ofoutputis l-(2/l X l/l)=l Maximum speed of output is l- (2/1 X 2/l =3 Now assume that in FIG. 14 D/C l/l then Minimum speed of output is Mean speed of output is Maximum speed of output is The formula for computing the varying angular velocity and acceleration of the output shaft are available in my U.S. Pat. No. 3,420,116, FIGS. 17,18,19 and 20.

The curves of FIGS. 5, 6, 7, 8, 9, 10, 11, 12 and 15 were traced by a computer which was programmed to compute the angular position of the compound elliptic gear for a corresponding position of the driving arm, its angular velocity and the angular velocity of the output shaft corresponding to a position ofthe driving arm.

A thrust bearing 36 is interposed between the frame 18 and the worm wheel 35. A worm 37 is fastened to a shaft 38 which is journalled in bearings 39 and 40, held respectively in brackets 41 and 42. Thrust bearings 43 and 44 are confined between collars 45 and 46 on shaft 38. a stop block 47 is fastened by means of screws 48 to the worm wheel 35. This block cooperates with a roller 49 under conditions to be described later. A counter weight 50 is fastened to arm 14 to balance gears 31 and 32.

THE DUCTOR MECHANISM A ductor roller 51 is journalled on levers 52 and 53 which are secured to the ductor operating shaft 54, the latter being journalled in bearings 55 and 56, which are attached to the press frame. A bellcrank 57 is also fastened to the shaft 54. A cam roller 58 is carried by one arm of this bellcrank 57 and the other arm carries the swivel block guide 59 thru which a spring guide rod 60 passes. This guide rod is provided with a unibal anchor 61 which is fastened to the frame of the press. A spring 62 bears against a nut 63 on the spring rod 60 and against the swivel block guide 59, thereby urging the roller 58 against the ductor cam 64.

A lever 65 is also fastened to the ductor operating shaft 54 and this lever 65 carries the roller 49 previously mentioned. At times it is desired that no ink should be ducted from the fountain roller 12 to the roller 51. In that case worm wheel 35 is rotated until stop block 47 can be contacted by roller 49, block 47 protruding far enough to prevent roller 51 from contacting fountain roller 12.

In FIG..1 is shown a small gear motor 66 and on its output shaft 67 the cam 64 and the sprocket 68 are mounted. A chain 70 connects 68 to sprocket 21, whereby driving effort is provided to shaft 15.

OPERATION OF THE MECHANISM An'elliptic gear pair produces a varying angular rotation of the driven gear when. the driving gear has a uniform angular Since the output speed varies from greater to less than the input speed there must occur during the rotationa condition where unity speed for both elliptic gears must occur.

Also, since uniform ducting of ink per cycle is important the ink fountain roller 12 must make one net revolution for each revolution of the arm 14, even though a momentary reversal of the roller during the cycle occurs.

As stated above this invention provided a simple solution to a very vexing problem when the ink fountain of a high-speed printing press becomes clogged. It has been learned from experience that heat-set inks have a tendency to clog the exit of the ink between the blade and fountain roller and thereby make it necessary to stop production and remove the accumulated matter.

However, a fountain roller receiving a periodic forward and then a backward motion serves the purpose of removing such matter away from the wedge shaped gap of the ink fountain.

A conventional ink fountain comprises a trough filled with ink and a roller immersed therein and from which the flow of ink is regulated by a blade almost contacting said roller to a ductor which after contacting the exposed portion of the. fountain roller transfers the ink to the distributing rollers of the printing press.

FIG. 1 shows a conventional ink fountain 10 which comprises end cheeks 11, an inclined blade (not shown) and the, fountain roller 12, thereby forming a trough which is adapted- 5 THE PLANETARY GEAR MECHANISM The planetary gear arm 14 is secured to a shaft 15 by means of the key 16. A ball bearing 17 supports shaft 15 on one end in the frame 18 and a cap 19 holds bearing 17 in place. Another ball bearing 20 supports the other end of shaft 15. A driving sprocket 21 is keyed to shaft 15, whereby arm 14 is continuously rotated in one direction. A nut 22 and a washer 23 confine sprocket 21, spacer 24 and ball bearing 17 to the shoulder 25 of shaft 15.

The fountain roller 12 is provided with a shaft extension 13 journalled in one of the cheek pieces 11 and with a longer extension 26 journalled in the frame 27. Extension 26 has mounted thereon a pinion 28 witha hub 29. Ball bearing 20 is supported in the hub 29. A jackshaft 30 is journalled in the planetary gear arm 14 and a gear 31 is keyed to shaft 30. Gear 31 meshes with the pinion 28. Similarily an elliptic gear 32 is also keyed to the shaft 30. Another elliptic gear 33 is fastened by means of screws 34 to the hub ofworm wheel 35, the latterbeing free to turn on shaft 15.

I claim:

1. An ink feeding mechanism having an ink fountain roller and a reciprocating ductor roller, said fountain roller disposed within a trough and actuated by a unidirectional drive means composed of a reverted planetary gear mechanism comprising in combination:

a. a frame having spaced supports provided with suitable bearings to receive shafts,

b. an input shaft journalled in some of the bearings held in said supports,

c. an arm secured to said input shaft,

d. a first elliptic gear integral with a first circular gear and rotatably mounted in said arm, e. a second elliptic gear held on said frame and meshing with said first elliptic gear,

f. an output shaft journalled in others of said bearings held composed of a reverted h. whereby said output shaft will receive a varying angular motion, comprising an angular forward motion in excess of 360 and an angular reverse motion equal to said excess and thereby resulting in a a net angular forward motion of exactly 360.

2. An ink feeding mechanism having an ink fountain roller and a reciprocating ductor roller, said fountain roller disposed within a trough and actuated by a unidirectional drive means planetary gear mechanism comprising in combination:

a. a frame having spaced supports provided with suitable bearings to receive shafts,

b. an input shaft journalled in some of the bearings held in said supports, an arm secured to said input shaft,

a first elliptic gear integral with a first circular gear and rotatably mounted in said arm,

e. a worm wheel rotatable on said input shaft,

. a second elliptic gear secured to said worm wheel and meshing with said first elliptic gear,

. an output shaft journalled in others of said bearings held in said spaced supports,

. a second circular gear secured to said output shaft and meshing with said first circular gear,

. a worm meshing with said worm wheel and mounted on a rotatable shaft,

. whereby said second elliptic gear may be rotated relative to said frame and thereby vary the angular contact of the ductor roller with the fountain roller.

3. An ink feeding mechanism as set forth in claim 2, in which the maximum speed ratio of said elliptic gears is greater than the ratio between said circular gears, whereby said output shaft will receive a varying angular forward motion and a lesser reverse motion per cycle.

4. An ink feeding mechanism as set forth in claim 2, having reciprocation of said ductor roller is interrupted.

5. An ink feeding mechanism as set forth in claim 2, wherein the combination of gearing imparts to the output shaft an acceleration value of item at the beginning and at the termination of the cyclic motion.

6. A viscous liquid feeding mechanism having a fountain roller and a reciprocating ductor roller, said fountain roller disposed within a trough and driven by a unidirectional drive means composed of a reverted planetary gear mechanism comprising in combination:

a. a frame having spaced supports provided with suitable bearings to receive shafts,

in addition a block fastened tosaid worm wheel, whereby the b. an input shaft journalled in some of the bearings held in.

said supports,

c. an arm secured to said input shaft,

d. a first elliptic gear integral with a first circular gear and rotatably mounted in said arm,

e. a second elliptic gear held on said frame and with said first elliptic gear,

f. an output shaft connected to said fountain roller and journalled in others of said bearings held in said spaced supports, and

g. a second circular gear secured to said output shaft and meshing with said first circular gear, the latter being onehalf the size of said first circular gear,

h. whereby said fountain roller will receive a varying forward motion of 360 and a small reverse angular motion.

meshing 

1. An ink feeding mechanism having an ink fountain roller and a reciprocating ductor roller, said fountain roller disposed within a trough and actuated by a unidirectional drive means composed of a reverted planetary gear mechanism comprising in combination: a. a frame having spaced supports provided with suitable bearings to receive shafts, b. an input shaft journalled in some of the bearings held in said supports, c. an arm secured to said input shaft, d. a first elliptic gear integral with a first circular gear and rotatably mounted in said arm, e. a second elliptic gear held on said frame and meshing with said first elliptic gear, f. an output shaft journalled in others of said bearings held in said spaced supports, and g. a second circular gear secured to said output shaft and meshing with said first circular gear, said second circular gear being one-half the size of said first circular gear, h. whereby said output shaft will receive a varying angular motion, comprising an angular forward motion in excess of 360* and an angular reverse motion equal to said excess and thereby resulting in a a net angular forward motion of exactly 360* .
 2. An ink feeding mechanism having an ink fountain roller and a reciprocating ductor roller, said fountain roller disposed within a trough and actuated by a unidirectional drive means composed of a reverted planetary gear mechanism comprising in combination: a. a frame having spaced supports provided with suitable bearings to receive shafts, b. an input shaft journalled in some of the bearings held in said supports, c. an arm secured to said input shaft, d. a first elliptic gear integral with a first circular gear and rotatably mounted in said arm, e. a worm wheel rotatable on said input shaft, f. a second elliptic gear secured to said worm wheel and meshing with said first elliptic gear, g. an output shaft journalled in others of said bearings held in said spaced supports, h. a second circular gear secured to said output shaft and meshing with said first circular gear, i. a worm meshing with said worm wheel and mounted on a rotatable shaft, j. whereby said second elliptic gear may be rotated relative to said frame and thereby vary the angular contact of the ductor roller with the fountain roller.
 3. An ink feeding mechanism as set forth in claim 2, in which the maximum speed ratio of said elliptic gears is greater than the ratio between said circular gears, whereby said output shaft will receive a varying angular forward motion and a lesser reverse motion per cycle.
 4. An ink feeding mechanism as set forth in claim 2, having in addition a block fastened to said worm wheel, whereby the reciprocation of said ductor roller is interrupted.
 5. An ink feeding mechanism as set forth in claim 2, wherein the combination of gearing imparts to the output shaft an acceleration value of zero at the beginning and at the termination of the cyclic motion.
 6. A viscous liquid feeding mechanism having a fountain roller and a reciprocating ductor roller, said fountain roller disposed within a trough and driven by a unidirectional drive means composed of a reverted planetary gear mechanism comprising in combination: a. a frame having spaced supports provided with suitable bearings to receive shafts, b. an input shaft journalled in some of the bearings held in said supports, c. an arm secured to said input shaft, d. a first elliptic gear integral with a first circular gear and rotatably mounted in said arm, e. a second elliptic gear held on said frame and meshing with said first elliptic gear, f. an output shaft connected to said fountain roller and journalled in others of said bearings held in said spaced supports, and g. a second circular gear secured to said output shaft and meshing with said first circular gear, the latter being one-half the size of said first circular gear, H. whereby said fountain roller will receive a varying forward motion of 360* and a small reverse angular motion. 